Twisting and spinning spindle with spindle brake



Nov. 12, 1968 K. BRISKEN ET AL 3,410,073

TWISTING AND SPINNING SPINDLE WITH SPINDLE BRAKE Filed Nov. 29, 1965 4 Sheets-Sheet 1 Nov. 12, 1968 K. BRISKEN ETAL 3,410,073

TWISTING AND SPINNING SPINDLE WITH SPINDLE BRAKE Fild Nov. 29, 1965 4 Sheets-Sheet 2 Nov. 12, 1968 BRlSKEN ET AL 3,410,073

TWISTING AND SPINNING SPINDLE WITH SPINDLE BRAKE Filed Nov. 29, 1965 4 Sheets-Sheet 5 7a M mazi 6 Nov. 12, 1968 K. BRISKEN ET AL TWISTING AND SPINNING SPINDLE WITH SPINDLE BRAKE Filed Nov. 29, 1965 4 Sheets-Sheet 4 FIG. 7

United States Patent 3,410,073 TWISTING AND SPINNING SPINDLE WITH SPINDLE BRAKE Kurt Brisken, Monchen-Gladbach, and Gustav Franzen, Neersen, near Krefeld, Germany, assignors to Palitex Project-Company G.m.b.H., Krefeld, Germany Filed Nov. 29, 1965, Ser. No. 510,288 Claims priority, applicat;%n6(1 6ermany, Dec. 4, 1964,

13 Claims. 3:1. 57-89) ABSTRACT OF THE DISCLOSURE The present invention relates to a spinning and twisting The present invention relates to a spinning and twisting spindle and, more specifically, to spindles of this type provided with a spindle brake in which each individual spindle is adapted to be stopped independently of an adjacent spindle to thereby permit the operator to carry out any desired operation on a spindle without interrupting the operation of another spindle. Such stopping of one spindle may be necessary for instance when an empty bobbin is to be replaced by a new bobbin or when a thread break has occurred.

Inasmuch as one operator usually has to attend to a great number of spindles, each operation to be carried out may cause an increase in the stopping period of the machine or machine part. On the other hand, an increase in the output of a spinning and twisting machine is dependent not only on the increase in the speed of the spindles but also on the number of stoppages which have to be effected by the operator. It is, therefore, the tendency to reduce the number of necessary manipulations to a minimum and to automate all operations as far as possible, so that the necessary stopping of a spindle will be effected without the operator.

In this connection, with uptwisters and two-for-one twisting machines, means have been provided for automatically stopping a spindle in response to a thread regulator actuating a spindle brake. The thread regulator is adapted in case of a thread break or in response to the bobbin becoming empty, to initiate a lifting movement of the winding bobbin from the friction roller so that also the winding bobbin comes to a standstill.

If in the case of a thread break or an exchange of the bobbin the spindle is stopped, the operator must remove those working elements from the spindle range which impede the new threading of the thread or the exchange of the empty bobbin. Such working element is for instance the thread guide which is arranged axially with regard to the spindle and which for technical reasons must be as close as possible to the spindle tip. With most machines, the thread guide is so arranged that it can be turned in a direction away from the machine so that it will get out of the range of the operator. After the respective operations have been carried out by the operator, the thread guide is manually returned to its working position.

It is an object of the present invention to provide a twisting or spinning machine with spindle brake and with 3,410,073 Patented Nov. 12, 1968 thread guide arranged axially above the spindle and adapted to be returned horizontally and/or vertically, which will make it possible independently of a thread guide automatically to brake the spindle by such a movement of the operator which the latter has to carry out at any rate when handling a spindle.

It is another object of this invention to connect the thread guide with the spindle brake in such a way that a movement of the thread guide out of its working position will automatically cause an engagement of the spindle brake which will automatically be disengaged when the thread guide is returned to its working position.

These and other objects and advantages of the invention will appear more clearly from the following specification in connection with the accompanying drawings, in Which:

FIG. 1 diagrammatically illustrates in section a portion of a spindle with spindle brake within the range of the spindle rail, and a thread guiding member axially arranged with regard to said spindle and adapted to be turned late-rally.

FIG. 2 is a partial top view of FIG. 1.

FIG. 3 is a horizontal section taken along the line III-III of FIG. 1.

FIG. 4 illustrates on a larger scale than FIG. 3 the right-hand central portion of FIG. 3.

FIG. 5 is a diagrammatic illustration of a two-for-one twisting spindle wtih a fluid-operable device for actuating the spindle brake and for lifting off the bobbin by turning the thread guiding member.

FIG. 5a shows a two-for-one twisting spindle with a fluid-operable device of a different design for lifting olf the winding bobbin and for stopping the spindle.

FIG. 5b illustrates on a somewhat larger scale than FIG. 5 the spindle brake within the whorl of FIG. 5.

FIG. 6 shows the electromagnetic brake 'for the whorl of FIG. 5a, the whorl being sectioned.

FIG. 7 diagrammatically illustrates a laterally turnable thread guiding member adapted to establish an electric contact for actuating the spindle brake.

Referring now to the drawings in detail, the arrangement shown in FIGS. 1 .and 3 comprises a spindle rail 1 provided with a supporting flange 2 within the range of a spindle generally designated 7, said flange 2 being shown in top view in FIG. 3. Mounted in the spindle rail 1 is the shaft 3 of spindle 7. Above spindle rail 1 braking jaws 4 extend around spindle shaft 3 and are adapted against the thrust of spring means to pivot outwardly about a pivot 5 (FIG. 3) so that the braking jaws will brakingly engage the braking surfaces 6 in the spindle whorl 7a. For purposes of pivoting the braking jaws 4 outwardly, a pivot 8 (FIG. 1) is provided with a spreading head 9 of rectangular cross-section, which extend between the braking jaws 4 and is adapted in response to a rotation of pivot 8 to spread the braking jaws 4 away from each other. For purposes of imparting a rotative movement upon pivot 8, the latter is supported by a lever arm 10 having a longitudinal slot 12a with a unilaterally widened portion 13, as shown in FIGS. 3 and 4. An .angle lever 11 connected to the lower end of a rotatable bar 14 has a slide bushing 12 connected thereto which in turn slidably engages said longitudinal slot 12a. Rotatable bar or rod 14 extends through flange 2 of the spindle rail in which it is rotatably guided. Bar or shaft 14 extends upwardly into the range of a thread guiding member 15 mounted upon the upper free end of rod 14 by means of a bushing 16. Below said bushing 16 rotatable rod 14 extends through a supporting bar 17 adapted to be clamped upon a machine element by means of bore 18 and a screw 19. Supporting arm 17 has that end thereof which faces the thread guiding member 15 provided with an abutment 20 by means of which the thread guiding member 15 is prevented from turning in one direction. When thread guiding member 15 engages abutment 20, the thread guiding member 15 occupies its working position in which the eye of the thread guiding member 15 is coaxial with regard to the spindle axis. Directly between supporting arm 17 and thread guiding member 15, rotatable rod 14 has connected thereto a follower disc 21 (FIG. 2) in the form of a sector of a circle. Any pivotal movement of said disc 21 is conveyed to rotatable bar 14. Said disc 21 has perpendicularly arranged thereon two follower pins 22 .and 23 located in spaced relationship to each other. The distance between said two pins 22 and'23 is less than the maximum pivoting movement of the thread guiding member 15 While, however, the difference takes into consideration the adaptation to the broadened section 13 of the longitudinal slot 12a in lever 10.

The spindle arrangement according to FIGS. 1 to 4 permits the following operation: It may be assumed that the arrangement occupies the position shown in full line in FIGS. 1 and 3 and that it is now desired to effect an operation on said spindle which will necessitates pivoting thread guiding member 15 out of its working position. To this end, the operator pivots the thread guiding member 15 toward the side while the spindle is rotating. More specifically, the operator pivots the thread guiding member 15 to that side which is permitted by the .abutment 20. During this pivoting movement the thread guiding member 15 engages the follower pin 23 so that with the pivoting of the thread guiding member 15, disc 20 will be pivoted. Accordingly, rotary rod 14 carries out a rotation in the direction indicated by the arrow 24 (FIG. 2). This rotation causes angle lever 11 to pivot so that its sleeve 12 which engages slot 12a will move from the inner end of said slot to the outer end into the broadened section 13. The two end positions of bushing 12 supported by angle lever 11 are shown in FIG. 3 once in full-lines and once in dash-lines. At the same time, FIG. 3 also shows the location of the eye of thread guiding member 15 after the pivoting operation has been effected. However, merely for reason of limited space, thread guiding member 15 is shown in close proximity to the axis of rotation of angle lever 11. The displacement of bushing 12 in slot 12:: also causes lever to pivot to the dash-line position shown mm FIG. 3, so that, as mentioned above, the braking jaws 4 are spread apart thereby permitting the spindle brake to become effective.

When the operator has completed his operations on spindle 7, the operator attending to the thread guiding member returns the thread guiding member to its starting position shown in FIG. 1. Shortly before the thread guiding member reaches the abutment 20, it will engage abutment pin 22 so that disc 21 is pivoted about a very slight angle. This tilting movement represents a corresponding movement of rotation of rotatable rod 14. This corresponding rotation of bar 14 will suflrce to lift bushing 12 out of the broadened section 13 in longitudinal slot 12a so that bushing 12, in conformity with FIG. 4, will move from its full-line positioninto its dash-line position of FIG. 4. By disengaging bushing 12 from its engaging or locking position, the above-mentioned spring means acting upon braking jaws 4 will move the latter toward each other or will urge braking ja ws 4 away from the braking surface 6 of whorl 7. As a result, pivot lever 10 returns to its starting position so that also a return movement of rod 14 to its starting position will occur. In this way, disc 21 moves into its full-line position shown -in FIG. 2.

As will be evident from the above, the turning movement of the thread guiding member 15 out of its Working position automatically causes a braking of the spindle.

A return pivoting of thread guiding member 15 to its working position will automatically cause the spindle brake to disengage, however, only after the thread guiding member 15 has practically reached its working position.

The embodiment of FIG. 5 shows the whorl 7a of the spindle, a balloon-confining member 95, and the thread guiding member 96. The thread is pulled upwardly from the yarn body arranged inside the balloon-confining member -and is then guided axially downwardly through the thread guiding member 96, whereupon it again leaves the balloon-confining member 95 as thread 60 in upward direction. In this way, the balloon tip is formed in the eye of the thread guiding member 15. The produced twist is then conveyed over a deviating roller 25 to the windingup bobbin 26 which latter is journalled in arms 27 and when tilting downwardly, rests on the driven friction roller 28. Directly ahead of the winding-up bobbin 26 there is located a thread guiding member 29 which is movable back and forth.

Supporting arm 27 which is tiltable upwardly and carries the winding-up bobbin 26 is linked at 30 to the machine frame. Pivotally connected to arm 27 at 31 is a piston rod 32 with a piston disc 33 which is axially displaeeable in a fluid operable cylinder 34. Piston rod 32 extends through said cylinder 34 and has its free end 35 pivotally connected to one end of a bar 36 the other end of which carries abutment means 37. Bar 36 extends through the brake operating lever 38 which at 39 is pivotally connected to spindle rail 40. The free end 41 of lever 38 is designed as elbow or manually operable lever for the brake. By tilting lever arm 41 downwardly or by moving the second arm 38 upwardly, braking rod 42 is moved downwardly thereby causing engagement of the spindle brake within whorl 7a similar to the arrangement of FIGS. 1-4. The spindle brake of FIG. 5 may be designed similar to the spindle brake according to FIGS. 1 to 4. The actuation of the brake rod 42 by lifting lever arm 38 is brought about by an upward movement of piston disc 33. To this end, one end of a tube or hose 43 leads into cylinder 34 below piston disc 33, whereas the other end of said tube or hose 43 is connected to a valve 44. Valve 44 communicates with a pressure fluid conduit 45 which extends in longitudinal direction of the machine. The thread guiding member 15 is connected to the pivot stud 46 of valve 44. Valve 44 is closed when thread guiding member 15 occupies its working position, shown in the drawing. In this instance, the tube or hose 43 is not under pressure. However, when thread guiding member 15 is pivoted laterally, valve 44 will move to its open position in which pressure fluid from pressure conduit 45 passes through tube or hose 43 into cylinder 34 below piston disc 33. Consequently, piston disc 33 will be lifted against the thrust of spring 33a. This lifting operation causes supporting arm 27 to move upwardly so that winding bobbin 26 will lift itself off the friction roller 28. Shortly before supporting arm 27 reaches its highest position, bearing 37 engages pivot arm 38 and tilts the latter somewhat upwardly thereby causing engagement of the spindle brake and braking of the whorl by the latter.

The turning of thread guiding member 15 thus brings about a stoppage of the winding-up bobbin 26 and also causes whorl 7a and thus spindle 7 to stop, whereby the operator will be able to carry out the desired operations on the stopped spindle, with the thread guiding member moved out of his way. By returning the thread guiding member 15 to its working position, valve 44 is vented so that piston disc 33 will in view of the thrust of spring 33a be moved downwardly. The downward speed of piston disc 33 may be controlled by a choke in valve 44. Braking rod 42 is pulled upwardly by a spring s, and thus, the spindle brake is disengaged and the spindle can again be rotated. Finally, the winding-up bobbin 26 will again engage friction roller 38 so that winding-up bobbin 26 will again be rotated.

The embodiment of FIG. 5a differs from that of FIG. 5 in the mounting of the spindle on the spindle frame and the means for stopping said spindle.

Similar to the embodiment of FIG. 5, a hose 43 leads from the valve to fluid pressure cylinder 34 below piston disc 33. Furthermore, below piston disc 33 cylinder 34 has connected thereto a hose 43a which leads into a pressure cylinder 34a behind the piston disc 33a thereof. Piston rod 32a is linked to a spindle support 82 which in its turn is at 83 linked to a stationary part of the machine frame so as to be tiltable upwardly. Spindle carrier 82 carries the spindle with its bearing housing 84 below balloon-confining means 95. Such spindle arrangement is disclosed, for instance, in patent application Ser. No. 495,815.

FIG. 5a shows the spindle 7 with spindle whorl 7a in engagement with the tangential driving belt 81 which in its turn engages rollers 80 journalled on rail 40. The illustrated spindle as shown in FIG. 5a occupies its Working position so that whorl 7a and thus spindle 7 are driven by the tangential driving belt 81. At the same time, the winding-up bobbin 26 rests on the friction roller 28.

When the thread guiding member 15 is turned laterally, this turning movement opens valve 44 so that pressure fluid passes from the central pressure conduit 55 through hose 43 into pressure cylinder 34 below piston disc 33. Piston disc 33 will thus be lifted in pressure cylinder 34 against the thrust of spring 33a so that through the intervention of piston rod 32, winding-up bobbin 26 is lifted off the friction roller 28. At the same time, pressure fluid also passes through hose 43a into pressure cylinder 34:! and against the thrust of spring 3311 displaces piston disc 33 and thus piston rod 32a. Consequently, spindle carrier 82 according to FIG. 5a tilting in clockwise direction and brings about a movement of the whorl 7a away from tangential driving belt 81. In this way, the drive of whorl 7a is interrupted, and the spindle comes to a standstill. A rapid stopping of the spindle will be aided by the fact that together with the disengagement of whorl 7a from tangential driving belt 81, whorl 7a and thus spindle 7 will be braked, for instance, by means of suitable magnets M.

When valve 44 is vented by returning thread guiding member 15 to its working position, piston discs 33 in pressure cylinders 34 and 34a will, due to the thrust of springs 33:: and 35a return to their starting position so that the spindle returns to its working position and winding-up bobbin 26 will again rest on friction roller 28. Inasmuch as the spindle must start its rotation prior to the winding-up bobbin 26 again starting its rotation, spring 33a is weaker than spring 33b so that the return of piston disc 33 in pressure cylinder 34a will start prior to the return of piston disc 33 in pressure cylinder 34. Instead of disengaging the spindle from its drive by turning it away from the tangential driving belt 81, it is, of course, also possible to move the spindle in the horizontal plane.

If the above operations are not initiated in response to the actuation of the thread regulator, they may be initiated by an upward movement of thread guiding member 15, i.e., independently of the thread regulator which, if desired, may also be omitted.

FIG. 8 illustrates a spindle braking arrangement in which the braking is initiated electrically through the intervention of a thread regulator 15a. The thread regulator 15a, which is adapted to be turned toward the side, has its connecting end located in a groove 71 of the support 72 for the thread regulator. Said thread regulator 15a is adapted to be lifted out of groove 71 by a turning movement. This lifting movement also brings about a lifting of leaf contact spring 75 which holds the thread regulator 15a in its operative position. Contact 73 of contact spring 75 is adapted to engage a contact spring 74. The supply of current is effected through a transformer 76. When the circuit between contacts 73 and 74 is closed in the manner metioned above, the spindle brake becomes effective. When the electromagnetic core 78 is drawn into coil 77 so that arm of spindle brake will be turned, the braking jaws 4 are spread outwardly and engage the braking surface of the spindle whorl 7a and thus brake the spindle whorl 7 and the spindle.

A signalling lamp 79 indicates when a twisting station is in braked condition. Lamp 79 is connected to the circuit in such a manner that it forms a series resistance with regard to the magnetic coils 77 of the electromagnet and thus protects said coil 77 against overload inasmuch as the resistance of the lamp 79 will increase with an increase in temperature.

When selecting the embodiment of FIG. 8, there may additionally be provided a thread control member which will become effective in such a manner that independently of the thread control a stopping of the thread brake and thus a lifting of the Winding-up bobbin can be effected by turning the thread regulator 15a. The machine may again be started by turning back the thread control member 15a while releasing the thread regulator.

It is, of course, to be understood that the present invention is, by no means, limited to the embodiments referred to above but also comprises any modifications within the scope of the appended claims.

What we claim is:

1. A textile spindle arrangement, especially for twisting and spinning machines, which comprises: rotatable spindle means, spindle brake means operable to brakingly engage and disengage said spindle means, thread guiding means manually and selectively movable from a working position to an ineffective position and vice versa, temporary locking means operable to hold said thread guiding means in its effective position, spring means continuously urging said thread guiding means to move to its working position, and control means operatively interconnecting said thread guiding means and said brake means and operable automatically in response to said thread guiding means moving out of its working position toward said ineffective position to move said spindle brake means into braking position for braking said spindle means, said control means also being operable automatically in response to said thread guiding means being moved out of its ineffective position toward its effective position to cause said braking means to disengage said spindle means to thereby permit resumption of the rotation of the spindle.

2. A textile spindle arrangement, especially for twisting and spinning machines, which comprises: rotatable spindle means, spindle brake means operable to brakingly engage and disengage said spindle means, thread guiding means manually and selectively movable from a working position to an ineffective position and vice versa, and con trol means operatively interconnecting said thread guiding means and said brake means and operable automatically in response to said thread guiding means moving out of its working position toward said ineffective position to move said spindle brake means into braking position for braking said spindle means, said control means also including latching means operable to hold said spindle brake means in braking position and said thread guiding means in its ineffective position, said latching means being operatively connected through said control means with the said thread guiding means to move into unlatching position in response to said guiding means moving toward its working position whereby said control means will be operative automatically in response to said thread guiding means being moved out of its ineffective position toward its effective position to cause said braking means to disengage said spindle means to thereby permit resumption of the rotation of the spindle.

3. A textile spindle arrangement, especially for twisting and spinning machines, which comprises: rotatable spindle means, spindle brake means operable to brakingly engage and disengage said spindle means, thread guiding means manually and selectively movable from a working position to an ineffective position and vice versa, and control means operatively interconnecting said thread guiding means and said brake means and operable automatically in responseto said thread guiding means moving out of its working position toward said ineffective position to move said spindle brake means into braking position for braking said spindle means, said control means including actuating lever means having one end operatively connected to said braking means for engaging the same, the other end of said actuating lever means being provided with slot means, slide means slidably engaging said slot means, rotatable rod means having one end operatively connected to said slide means and having its other end connected to said thread guiding means for turning movement in response to a movement of said thread guiding means from its working position toward its ineffective position whereby said control means will be operable automatically in response to said thread guiding means being moved out of its ineffective position toward its effective position to cause said braking means to disengage said spindle means to thereby permit resumption of the rotation of the spindle.

4. A textile spindle arrangement, especially for twisting and spinning machines, which comprises: rotatable spindle means, spindle brake means comprising brake shoes operable to brakingly engage and disengage said spindle means, thread guiding means manually and selectively movable from a working position to an ineffective position and vice versa, control means operatively interconnecting said thread guiding means and said brake shoes and including pivotable lever means comprising means extending between two adjacent ends of said brake shoes and operable automatically in response to said thread guiding means moving out of its working position toward said ineffective position to bring about movement of said brake shoes into braking position for braking said spindle means, and spring means associated with said adjacent brake shoe ends and continuously urging said brake shoes into non-braking position, whereby said control means will automatically in response to said thread guiding means being moved out of its ineffective position toward its effective position cause said brake shoes to disengage said spindle means to thereby permit resumption of the rotation of the spindle.

5. An arrangement according to claim 4, in which said control means includes fluid operable cylinder piston means operatively connected to said spindle brake means for actuating the latter in response to a movement of said thread guiding means from its working position toward its ineffective position.

6. An arrangement according to claim 5, in which said fluid operable cylinder piston means comprises a movable member, and which includes link means operatively connecting said movable member with said spindle brake means.

7. An arrangement according to claim 4, which includes: supporting means, movable spindle holding means supported by said supporting means, driving belt means normally drivingly engaging said spindle means for driving the same, fluid operable cylinder piston means operatively connected to said spindle holding means and operable in response to the supply of pressure fluid thereto to move said spindle holding means to a position for interrupting driving engagement of said belt means with said spindle means, valve means operatively connected to said thread guiding means and operable in response to the latter moving out of its working position to convey pressure fluid to said cylinder piston means, and means associated with said cylinder piston means for continuously urging said holding means into position for holding said spindle means in driving engagement with said belt means.

8. An arrangement according to claim 4, in which said brake means includes electromagnetic means for actuating the same, and in which said control means includes normally open electric circuit means associated with said electromagnetic means and adapted to be closed in response to said thread guiding means moving from its working position to its ineffective position to thereby energize said electromagnetic means for actuating said brake means.

9. An arrangement according to claim 8, in which said thread guiding means comprises resilient contact means operable yieldably to hold said thread guilding means in its Working position and also operable in response to said thread guiding means being moved out of its working position to close said electric circuit means.

10. An arrangement according to claim 8, in which said electric circuit means includes signalling means operable to emit a signal in response to the energization of said electric circuit means.

11. An arrangement according to claim 4, which includes drivable bobbin means for winding up thread means from a bobbin on said spindle means, and means operatively connecting said thread guiding means with said bobbin means and operable in response to said thread guiding means moving out of its working position to interrupt the drive of said bobbin means.

12. An arrangement according to claim 4, which includes: winding-up bobbin means for receiving thread from a bobbin on said spindle means, driving means for driving said winding-up bobbin means, second control means operatively interconnecting said thread guiding means and said winding-up bobbin means and operable in response to the movement of said thread guiding means from its working position to its ineffective position to interrupt driving connection between said driving means and said winding-up bobbin means, and retarding means interposed between said second control means and said thread guiding means for delaying the re-establishment of the driving connection between said driving means and said Winding-up bobbin means with regard to the disengagement of said brake means from said spindle means.

13. An arrangement according to claim 4, which includes: Winding-up bobbin means for receiving thread from a bobbin on said spindle means, said winding-up bobbin means being movable from an effective position in which it carries out a winding-up operation to an ineffective position in which it does not carry out a windingup operation, and vice versa, first fluid operable cylinder piston means operable in response to the supply of pressure fluid thereto to move said winding-up bobbin means to said ineffective position, first spring means associated with said first fluid operable cylinder piston means and continuously urging said winding-up bobbin means into said effective position, driving means for driving said spindle means, said spindle means and said driving means being movable relative to each other into and out of driving engagement with each other, second fluid operable cylinder piston means forming part of said control means and operable in response to the supply of pressure fluid thereto to move said spindle means and said driving means out of driving engagement with each other, second spring means associated with said second fluid operable cylinder piston means and continuously urging said spindle means and said driving means into driving engagement with each other, and valve means operable in response to said thread guiding means moving out of its working position to convey pressure fluid to said first and second fluid operable cylinder piston means, said second spring means being stronger than said first spring means.

References Cited UNITED STATES PATENTS 855,162 5/1907 Cook 5788 957,453 5/1910 Isleib 5761 2,482,654 9/1949 Cocharan et al. 2,599,256 6/1952 Hartley et a1. 5784 2,786,324 3/1957 Keith et a1 57-80 X 2,930,182 3/1960 Lenk 5784 2,975,584 3/1961 Makant et a1 5780 X 2,972,219 2/1961 Collins 5788 WILLIAM S. BURDEN, Primary Examiner. 

